EP0350678B1 - Kugelgelenk - Google Patents

Kugelgelenk Download PDF

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Publication number
EP0350678B1
EP0350678B1 EP89111377A EP89111377A EP0350678B1 EP 0350678 B1 EP0350678 B1 EP 0350678B1 EP 89111377 A EP89111377 A EP 89111377A EP 89111377 A EP89111377 A EP 89111377A EP 0350678 B1 EP0350678 B1 EP 0350678B1
Authority
EP
European Patent Office
Prior art keywords
ribs
bearing shell
joint
ball
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89111377A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0350678A2 (de
EP0350678A3 (de
Inventor
Günther Henkel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TRW Fahrwerksysteme GmbH and Co KG
Original Assignee
TRW Fahrwerksysteme GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TRW Fahrwerksysteme GmbH and Co KG filed Critical TRW Fahrwerksysteme GmbH and Co KG
Publication of EP0350678A2 publication Critical patent/EP0350678A2/de
Publication of EP0350678A3 publication Critical patent/EP0350678A3/de
Application granted granted Critical
Publication of EP0350678B1 publication Critical patent/EP0350678B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/068—Special features relating to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
    • F16C11/0619—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part comprising a blind socket receiving the male part
    • F16C11/0623—Construction or details of the socket member
    • F16C11/0628—Construction or details of the socket member with linings
    • F16C11/0633—Construction or details of the socket member with linings the linings being made of plastics
    • F16C11/0638—Construction or details of the socket member with linings the linings being made of plastics characterised by geometrical details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/102—Construction relative to lubrication with grease as lubricant

Definitions

  • the invention relates to a ball joint for motor vehicles, with a bearing shell made of an elastic plastic inserted between a joint housing and a ball head of a rotatable and tiltable ball pin, which is supported with ribs on its outside in the joint housing, under the influence of a joint preload or load lubrication pockets are formed on the inside of the bearing shell in the areas lying between the ribs.
  • DE-B-24 34 490 discloses a ball joint with a hard elastic inner shell, which is carried by a material elastic outer shell.
  • the outer shell is in turn supported by meridional ribs in the joint housing, so that the bearing surface can bend between the ribs. This in turn creates meridional lubrication pockets, with the disadvantage of lubrication, which is worse for tilting movements than for rotary movements.
  • DE-A-36 39 963 discloses a ball joint for transmission linkages in motor vehicles with a plastic bearing shell inserted between a plastic joint housing and a ball head, the bearing shell engaging undercuts on the inner wall of the joint housing with projections on its jacket.
  • the projections of the bearing shell can be inserted into grooves in the inner wall of the joint housing, which extend from an end face of the joint housing in the journal axis direction, and can be screwed through openings in the groove flanks into recesses in the inner wall of the joint housing, the essentially circumferential boundary walls of which provide undercuts for supporting the Form projections.
  • the object of the invention is to create a ball joint with improved joint lubrication, which in particular has more uniform tilting and torque and the production of which is less complex.
  • the ribs of the bearing shell are wound obliquely with respect to the axis of the joint (axis of the untilted ball pin).
  • the ribs therefore run in the circumferential direction around the joint axis and additionally in the direction of the joint axis.
  • the bearing shell between the ribs deforms under the influence of a preload or a load.
  • winding lubrication pockets are also formed in the bearing surface between the ribs. This enables the bearing surfaces under the ribs to be greased both during a tilting movement and during a rotating movement of the ball pin.
  • the lubrication pockets are in fact arranged in the joint axis direction as well as in the circumferential direction on both sides of the bearing surfaces located below the ribs.
  • the bearing shell provided with the spiral ribs consists of a hard elastic plastic, in particular of an acetal resin.
  • the hard elastic bearing shell is subject to only a slight deformation between the ribs, so that smooth transitions between the lubrication pockets and the bearing surfaces under the ribs occur, which favor a coherent lubricating film.
  • the ribs of the bearing shell are evenly distributed around the hinge axis, so that the moments are relatively independent of the direction of the load on the ball pin.
  • the independence from the direction of loading of the ball pin is further improved if all the ribs are wound in the same direction. In this way, lubrication pockets of the same shape and size can be produced between pairs of ribs.
  • the ball head transports grease from the lubrication pockets into the lubrication pocket with each tilting movement Storage areas under the ribs.
  • Four ribs wound around the hinge axis may be sufficient for permanent and even hydrodynamic lubrication.
  • the ribs start approximately tangentially from an edge of a deflection opening of the bearing shell for the ball pivot, so that the lubrication pockets around the edge of the deflection opening are less pronounced. This prevents larger amounts of the grease from being pressed out of the passage opening when the ball pivot is tilted.
  • the lubricating effect according to the invention is achieved at least in the case of load directions which press the ball head against the ribbed bearing surface areas.
  • the ribs are arranged on a spherical section of the bearing shell and are supported on a spherical housing receptacle.
  • the bearing shell therefore has a constant and relatively small wall thickness between the ribs, so that the desired lubrication pockets can form.
  • the bearing shell additionally has meridional ribs, which each start from one end of a sinuous rib and whose extension in the joint axis direction corresponds approximately to that of the sinuous ribs. In this way, the number of lubrication pockets is doubled with relatively short ribs.
  • the bearing shell can be produced with a relatively simple injection mold if the side walls of the ribs are aligned in the direction of the joint axis. During manufacture, the outer shape and core stamp of the injection mold can simply be pulled apart in the direction of the joint axis.
  • the bearing shell is formed in two parts, an outer bearing shell provided with ribs wound around the hinge axis having a recess on the end face for a soft, elastic inner bearing shell.
  • the outer shell ensures ideal lubricant distribution and the flexible inner shell adjusts the preload of the ball head.
  • the improved lubricant distribution and the defined preload of the ball head result in an excellent compensation of component tolerances.
  • the bearing shell In order to facilitate the desired deformation of the bearing shell during assembly, it can have meridional slots that start from the deflection opening for the ball stud. When the ball head is inserted, it is easier to expand and overstressing the bearing shell material is avoided.
  • the meridional slots preferably extend approximately up to an equatorial plane of the spherical head which runs perpendicularly through the axis of the joint, so that when it is inserted into the bearing shell it only covers a region of the bearing shell which can be easily expanded.
  • the ribs are arranged between the closed end face of the bearing shell and the circumferential line determined by the end of the slots in a practical development, so that the entire sliding surface is supplied with the lubricant relatively evenly.
  • the bearing shell has two groups of ribs which are arranged on different sides of a plane running perpendicular to the axis of the joint and are wound in different directions, whereby the lubricant is conveyed in a helical line out of the bearing shell at one Rotational movement of the ball pin is hindered.
  • the joint housing 4 receives the bearing shell 3 in a housing receptacle 5, which is spherical to a housing opening 6 for the ball pin 1.
  • the housing receptacle 5 is closed on the end face opposite the housing opening 6 by a rolled-in closure cover 7.
  • the closure cover 7 defines a peripheral edge flange 8 of an outer bearing shell 9 in the joint housing.
  • the outer bearing shell 9 is made from a hard elastic material, in particular from an acetal resin such as polyoxymethylene (POM), and has ribs on the outside, which will be discussed later.
  • An inner bearing shell 11 is inserted into a recess 10 of the outer bearing shell 9 on the closure cover side, which is located on the end face of the closure cover 7 supports.
  • the inner bearing shell 11 is made of a soft, elastic material, in particular of polyurethane (PUR) and defines the preload of the ball head 2 used. As can be seen better from FIG. 2, the form elasticity of the inner bearing shell 11 is increased by end support ribs 12, which deform elastically under the pressure of the closure cover 7.
  • the ball pin 1 is inserted through a passage opening 14 of the outer bearing shell 9, so that it protrudes from the housing opening 6 such that it can rotate and tilt.
  • the inner bearing shell 11 is inserted into the recess 10 of the outer bearing shell 9 and placed on the ball head 2. Finally, the bearing shell parts and the ball pin are secured by rolling the sealing cover 7 into the joint housing 4.
  • the outer bearing shell 9 is also cylindrical on the outside. There it connects the edge flange 8 with its externally spherical section provided with the ribs 13. Since the ribbed section has a spherical bearing surface 15 for the ball head 2 on the inside, it has a constant wall thickness between the ribs 13, which favors the formation of lubrication pockets. If the outer bearing shell 9 is inserted into the joint housing 4 and especially if the ball head 2 presses against the bearing surface 15 under pretension, the thin-walled areas between the ribs 13 bulge out and form lubrication pockets.
  • ribs 13 are evenly distributed around the hinge axis.
  • the ribs 13 extend almost tangentially from the passage opening 14 and are wound in the same direction around the axis of the joint.
  • the ribs 13 run both in the circumferential direction around the joint axis and in the joint axis direction. Due to the spherical design of the ribbed section of the outer bearing shell 9, the ribs 13 also extend in the radial direction, so that they form spiral sections in the bottom view.
  • Each of the ridges extends over an angle of almost 90 ° about the pivot axis so that the ribs have a combined angular sum of almost 360 o about the hinge axis.
  • Four lubrication pockets arranged spirally around the hinge axis can thus form between the ribs 13. The number and position of the ribs 13 therefore necessitate large, uniform lubrication pockets.
  • the height of the ribs 13 is chosen so low that between the lubrication pockets and the bearing surface 15 under the ribs 13 there is a flat transition which enables the lubricant to be easily drawn into the bearing surface 15 under the ribs 13.
  • the ribs 13 are perpendicular to the outer surface of the outer bearing shell 9 with their side walls 16, so that the ribs 13 are favorably loaded under the influence of the radial forces.
  • the side walls 16 are aligned in the direction of the joint axis.
  • the meridional ribs 17 double the number of lubrication pockets and thus improve the lubricating effect without the bearing surface 15 under the ribs 13 and 17, which is problematic for greasing, being particularly enlarged.
  • the ball joint has a one-piece bearing shell 18, which is provided with three slits 19 extending from the deflection opening for the ball pin 1.
  • the slots 19 extend in the meridional direction up to approximately an equatorial plane of the ball head 2 running perpendicularly through the joint axis.
  • bearing shell 18 is provided on its outside with a group of three first ribs 20 which, starting from the passage opening 14, are wound clockwise around the axis of the joint and also extend approximately to an equatorial plane of the ball head 2 running perpendicularly through the axis of the joint, without to cut the meridional slots 19.
  • the bearing shell 18 On its closed end face, the bearing shell 18 is frustoconical, being on a cone 21 of the Truncated cone has a group of three second ribs 22 which are wound in opposite directions to the first ribs 20 about the axis of the joint.
  • the joint housing 8 is closed by means of a rolled-in closure cover 23, the shape of which is adapted to the frustoconical end face of the bearing shell 18 and which causes the same to be centered in the joint housing 8.
  • the bearing shell 18 can also be produced from the materials already specified above for the bearing shell 3.
  • lubrication pockets are formed in each case between the first ribs 20 and the second ribs 22 and between these two spaced-apart groups of ribs 20, 22, which bring about a uniform lubrication of the sliding surface of the ball head 2. Due to the opposing design of the first ribs 20 and second ribs 22, spiral transport of the lubricant out of the passage opening 14 of the bearing shell 18 is avoided. An additional lubricating effect is achieved by the lubricating groove-forming slots 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Pivots And Pivotal Connections (AREA)
EP89111377A 1988-07-14 1989-06-22 Kugelgelenk Expired - Lifetime EP0350678B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3823777 1988-07-14
DE3823777A DE3823777C1 (enrdf_load_stackoverflow) 1988-07-14 1988-07-14

Publications (3)

Publication Number Publication Date
EP0350678A2 EP0350678A2 (de) 1990-01-17
EP0350678A3 EP0350678A3 (de) 1991-02-20
EP0350678B1 true EP0350678B1 (de) 1993-07-21

Family

ID=6358603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89111377A Expired - Lifetime EP0350678B1 (de) 1988-07-14 1989-06-22 Kugelgelenk

Country Status (2)

Country Link
EP (1) EP0350678B1 (enrdf_load_stackoverflow)
DE (2) DE3823777C1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7985034B2 (en) 2004-02-12 2011-07-26 Raufoss Technology As Ball joint and bearing shell

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4108219A1 (de) * 1991-03-14 1992-09-17 Lemfoerder Metallwaren Ag Lagerschale aus kunststoff fuer kugelgelenke in kraftfahrzeugen und arbeitsverfahren zur herstellung eines kugelgelenks mit einer solchen lagerschale
DE4226986C2 (de) * 1992-08-14 2003-09-25 Audi Ag Gelenk, insbesondere Kugelgelenk
DE4338916C1 (de) * 1993-11-15 1995-05-04 Trw Fahrwerksyst Gmbh & Co Kugelgelenk
DE29722507U1 (de) * 1997-12-20 1999-04-22 Sachsenring Automobiltechnik AG, 08058 Zwickau Kugelschale für ein Kugelgelenk und Kugelgelenk mit einer solchen Kugelschale
DE19832254C2 (de) * 1998-07-17 2000-10-12 Sachsenring Entwicklungsgesell Kugelgelenk und Verfahren zu dessen Herstellung
FR3055040B1 (fr) 2016-08-12 2019-05-17 Lisi Aerospace Capuchon lubrifiant, fixation comprenant un tel capuchon et procede d'assemblage en interference

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5344980B2 (enrdf_load_stackoverflow) * 1973-11-06 1978-12-02
JPS529781B2 (enrdf_load_stackoverflow) * 1973-11-29 1977-03-18
DE3326960C2 (de) * 1983-07-27 1991-08-01 TRW Ehrenreich GmbH & Co KG, 4000 Düsseldorf Kugelgelenk
DE3530633A1 (de) * 1985-08-28 1987-03-05 Trw Ehrenreich Gmbh Kugelgelenk
DE3619004C1 (en) * 1986-06-05 1987-12-17 Trw Ehrenreich Gmbh Ball-and-socket joint
DE3639963A1 (de) * 1986-11-22 1988-06-01 Trw Ehrenreich Gmbh Kugelgelenk

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7985034B2 (en) 2004-02-12 2011-07-26 Raufoss Technology As Ball joint and bearing shell
DE112005000333B4 (de) * 2004-02-12 2017-11-23 Raufoss Technology As Kugelgelenk und Lagerschale

Also Published As

Publication number Publication date
DE58904946D1 (de) 1993-08-26
EP0350678A2 (de) 1990-01-17
DE3823777C1 (enrdf_load_stackoverflow) 1989-11-23
EP0350678A3 (de) 1991-02-20

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